Clutch brake with liquid and air cooling

ABSTRACT

A clutch-brake unit comprising a relatively fixedly mounted support structure, a drive shaft rotatable relative to the support structure, a housing rotatable relative to the support structure and at least partially surrounding the shaft, a brake within the housing and adapted for non-rotatably connecting the shaft to the support structure, a clutch within the housing for drivingly connecting the housing with the shaft, and actuating means for selectively energizing the clutch while simultaneously releasing the brake and vice versa. The housing is at least partially filled with lubricating fluid wherefrom heat is adapted to be transferred by contact with the housing and a driving member connected therewith.

United States Patent 1191 Sommer 1 1 Jan. 30, 1973 541 CLUTCH-BRAKE WITHLIQUID AND 3,020,990 2/1962 Liv ..192 1s A AIR COOLING 2,193,068 3 1940Keck .192 18 A 2,785,781 3/1957 Johansen ..l92/1 l3 A X lnvenwrr GordonSvmmer, GYOSSB Pomte 2,966,245 12/1960 Judge ..192 1s A WOOdS, Mich.3,177,994 4/1965 Jewson ..192/18 A [73] Assignee: Sommer Co., Inc.,Detroit, Primary Examiner Benjamin w wyche 1C Attorney-J. King Harnesset al. [22] Filed: Aug. 2, 1971 [21] Appl. No.: 167,990 [57] ABSTRACT Aclutch-brake unit comprising a relatively fixedly Related pp Dam mountedsupport structure, a drive shaft rotatable [63] Continuation-in-part ofScr. No. 804,771, March 6, rclmfvc to the suppcn Structure a housmgrotatable 1969 Pat' NO. 3 614 999 relative to the support structure andat least partially surrounding the shaft, a brake within the housing andLS. Cl. A B E adapted for IIOII-IOtfltflbi) COIIIICCIiIIg the shaft [0the 51 1111.0 Fl6d 67/04 SPPOrt Structure, a dutch within the housingfor [58] Field gk i A 6 87 17 113 A drivingly connecting the housingwith the shaft, and actuating means for selectively energizing theclutch while simultaneously releasing the brake and vice versa. Thehousing is at least partially filled with lubricat- [56] References cuedin fluid wherefrom heat is ada ted to be transferred g P UNITED STATESPATENTS by contact with the housing and a driving member connectedtherewith. 3,494,450 2/1970 Mankowsky ct a1 192/18 A 2,441,543 5/1948Longfield ..192/18 A 10 Claims, 5 Drawing Figures 1/4 W] WWI/4 [141W {/4ill 1/; 4 Ww/ m f Z474 J 7 74 I if! fl/ili 7);]; I 9? 7 M 3 m A7174, gfl j All 1 If i/ J 1 ,1 Q m 7/ 7// w I74 l/v a 1/ 1/ 9; 1/2 I 4 L l r aU w KW 40 9 /2 5' I /7/ 4 4' ,wm'ni m' PATENTEflJAuso I975 SHEEI 2 [IF 4CLUTCH-BRAKE WITH LIQUID AND AIR COOLING CROSS REFERENCE TO PRIORAPPLICATION This application is a continuation-in-part of US.application, Ser. No. 804,771, filed Mar. 6, 1969, and now US. Pat. NO.3,614,999, for Clutch and Brake with Cooling Means. The above indicatedapplication is assigned to the assignee of the subject application.SUMMARY OF THE INVENTION This invention relates generally toclutch-brake units and, more particularly, to a new and improved oilcooled clutch-brake unit adapted particularly, although not necessarily,for use in operative association with punch presses and the like.

It is accordingly a general object of the present invention to provide anew and improved clutch-brake unit.

It is a more particular object of the present invention to provide a newand improved clutch-brake unit that is extremely small or compact insize.

It is another object of the present invention to provide a new andimproved clutch-brake unit that utilizes a plurality of oil submergedfriction disc torque transmitting elements which will exhibit aminimalamount of wear by virtue of the fact that the torque transmittingfunction is achieved by the shearing of oil interjacent the discs.

It is still another object of the present invention to provide a new andimproved clutch-brake unit of the above character that can be operatedat high speeds and at high cyclic rates as a result of a low driveinertia and an effective oil cooling medium.

It is a further object of the present invention to provide aclutch-brake unit wherein the clutch and brake functions aremechanically interlocked, whereby to prevent damage to the unit due toimproper timing.

It is yet another object of the present invention to provide aclutch-brake unit of the above described type that features a balancingchamber for the pressurized air actuated piston thereof, whereby tominimize piston displacement during cyclic operation of the unit.

It is another object of the present invention to provide a new andimproved clutch-brake unit that will find universality of application.

Further important objects of the present invention are to provide a newand improved clutch-brake unit which is simple in design, economical toproduce and operate, extremely rugged and maintenance-free duringoperation, and wherein the input and output shafts thereof are readilyadapted for mounting to any associated machine, gears, sheaves,couplings, etc.

It is yet a further object of the present invention to provide a new andimproved clutch-brake unit that is adapted to be mounted directly withinthe hub of a rotating member, such as, for example, a rotatable flywheelor the like.

It is still a further object of the present invention to provide a newand improved clutch-brake unit that is adapted to fail safe, i.e., inthe braked condition, upon loss of pressure of the actuating medium.

Other objects and advantages of the present invention will becomeapparent from the following detailed description taken in conjunctionwith the accompanying drawings.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a longitudinal sideelevational view, partially broken away, of a preferred first embodimentof a clutch-brake unit embodying the principality of the presentinvention;

FIG. 2 is an end elevational view of the left end of the first preferredunit illustrated in FIG. 1;

FIG. 3 is an enlarged longitudinal cross-sectional view of the firstpreferred clutch-brake unit illustrated in FIG. 1;

FIG. 4 is a side elevational view of a typical machine with which thefirst preferred clutch-brake unit of the present invention may beoperatively associated, and

FIG. 5 is a partial enlarged longitudinal cross-sectional view of apreferred second embodiment of a clutch-brake unit also embodying theprincipality of the present invention.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Generally speaking,the clutch-brake unit of the present invention is adapted to findparticularly useful application in connection with the flywheel or asimilar rotatable member of a metal forming or stamping press or thelike. Although the present invention will find varied use in many othertypes of applications, as will more particularly be described, due tothe especially useful application of the present invention with atypical rotary flywheel, the present invention is shown and described,by way of example, in operative association therewith.

Referring now in detail to the drawings and in particular to FIGS. 1 and3, a first embodiment of a clutchbrake unit 10, in accordance with thepresent invention, is shown generally as comprising a rotatable housing12 having a pair of end wall members 14 and 16 which are spaced axiallyor longitudinally along a rotatable drive shaft, generally designated bythe numeral 18. The housing 12 forms an inner hub assembly foroperatively connecting a rotatable flywheel, generally designated 20, tothe shaft 18, with the flywheel 20-comprising an outer peripheral,relatively massive, section 22 having a plurality of axially spaced,radially inwardly extending V-belt receiving grooves 24 formed in theouter side thereof. The section 22 of the flywheel 20 is formed with anintegral, radially inwardly extending web or spoke section 26 thatterminates at its radially innermost portion in an axially extendingannular sleeve or collar section 28 defining a central axially extendingbore 30 spaced radially outwardly from the periphery of the shaft 18 anddefining one marginal wall portion of an internal cavity 32 within whichare located the clutch and brake elements of the present invention. Oneaxial end of the cavity 32 is closed by the end wall 16 which is fixedlysecured by suitable screws, bolts or the like 34 to the flywheel section28, with suitable O-ring sealing means or the like 36 being providedbetween an annular, axially extending shoulder 38 formed on the wallmember 16 and the axially outer end of the periphery of the bore 30, asbest seen in FIG. 3. The end of the cavity 32 opposite that which isclosed by the end wall member 16 is adapted to be closed by the end wallmember 14 and a generally axially and radially outwardly extendingenclosure member, generally designated by the numeral 40. The member 40is formed with a radially inwardly extending flange section 42 at oneaxial end thereof, which section 42 is fixedly secured by means of aplurality of circumferentially spaced, axially extending suitablescrews, bolts or the like 44 to a radially outwardly projecting shoulder46 formed around the outer periphery of the member 14, suitablefluid-tight gasket means 48 being provided between the confronting sidesof the sections 42 and 46. The opposite end of the member 40 is formedwith an axially extending section 50 adapted to bear against an annular,axially extending recess 52 formed around the inner periphery of theflywheel section 28, with suitable O-ring sealing means or the like 54being provided interjacent the confronting surfaces of the section 50and recess 52 to provide a fluid-tight seal therebetween. The member 40is formed with a radially outwardly extending flange section 56 directlyadjacent the section 50 thereof, which section 56 is formed with aplurality of circumferentially spaced, axially extending openings 58through which a plurality of axially extending screws, bolts or the like60 extend and are threadably received within suitable threaded bores 62in the flywheel 20 for rigidly securing the member 40 thereto. Themembers 16 and 40 are preferably provided with circumferentially space,axially extending ribs or fins, generally designated 64 and 66, forpurposes of heat dissipation, as will later be described in detail.

The end wall member 14 defines a central opening 68 which is arrangedcoaxially of the drive shaft 18 and the periphery of which is spacedradially outwardly from the outer surface of the drive shaft 18.Disposed between the inner periphery of the opening 68 and the outerperiphery of the drive shaft 18 is an annular, axially extending supportmember, generally designated by the numeral 70. The inner end of themember 70 extends axially inwardly from the end wall member 14 anddefines an annular axially extending shoulder 72 upon which the innerrace of an anti-friction bearing assembly 74 is mounted. The outer raceof the assembly 74 abuts against an annular shoulder 76 defined aroundthe inner periphery of the member 14, with the result that the members14 and 40, and thus the entire flywheel 20, is rotatably supportedrelative to the support member 70. As best seen in FIGS. 1 and 3, themember 70 is adapted to be fixedly secured by means of suitable screws,bolts, or the like 78 to an associated non-rotatable structure,generally designated 80, which functions to support the entire adjacentend of the clutch-brake unit embodying the present invention. Thestructure 80 may be of any suitable construction which is of arelatively rugged, heavyduty design as is necessary and conventional inrotatably supporting the flywheel 20 which may typically be in the orderof several thousand pounds in weight Together with carrying the bearingassembly 74, the support member 70 also supports another anti-frictionbearing assembly, generally designated 82, the inner race of which isengaged with an annular shoulder 84 formed around the adjacent end ofthe drive shaft 18, and the outer race of which is received within anannular recess 81 formed around the inner periphery of the supportmember 70. The bearing assembly 82, together with suitable fluid sealingmeans, such as an annular lip seal or the like 86,

is positively retained in place in the end of the support member bymeans of a suitable retaining plate 88 which is fixedly secured to theaxially outer side of the member 70 by means of a plurality of suitablecircumferentially spaced, axially extending screws, bolts or the like90. Preferably, suitable O-ring sealing means or the like 92 is providedbetween the outer periphery of the retaining plate 88 and the innerdiameterof the support member 70, as illustrated. The inner race of thebearing assembly 82 is also preferably secured upon the inner end of thedrive shaft 18 by being axially compressed between a radially outwardlyextending abutment wall 94 defined by the shaft 18 and a suitableretaining ring 96 that is threadably received upon externally threadedsection 98 of the shaft 18.

The end wall member 16 defines a central opening 100 that is coaxiallyaligned with the opening 68 and through which one end of the drive shaft18 extends. The shaft 18 is rotatably supported relative to theopening'100 by means of an anti-friction bearing assembly 102, the innerrace of which is secured to the shaft 18 by means of a pair of retainingrings 104 and 106, the latter vof which may be threadably received upona suitable externally threaded section 108 of the shaft 18. The outerrace of the bearing assembly 102 is adapted to be axially compressedbetween an annular shoulder 110 formed around the periphery of theopening 100 and an annular clamping ring 112 that is fixedly secured bya plurality of circumferentially spaced axially extending screws, bolts,or the like 114, to the axially outer side of the end wall member 16,with suitable O-ring sealing means or the like 116 being providedbetween the radially outer side of an axially extending shoulder 118 onthe ring 112 and the periphery of the opening 100. Also, suitable lipsealing means or the like 120 is provided between the inner periphery ofthe clamping ring 112 and the outer. periphery of the retaining ring104.

The drive shaft 18 extends axially outwardly from the end wall 16 and isprovided, at the axially outer end thereof, with a suitable pinion gear,generally designated 122, which may be secured upon a reduced diametersection 124 of the shaft 18 by means of a suitable retaining ring 126received upon an externally threaded portion 128 of the shaft 18. Thepinion gear 122 is preferably keyed in a conventional manner to theshaft Band is designed to transmit motive power from the flywheel 20 toan associated gear in a manner hereinafter to be described. The end ofthe shaft 18, between the end wall member 16 and pinion gear 122, isadapted to be rotatably supported upon a suitable support section 130 ofthe support structure 80 that is disposed upon the axially opposite sideof the housing 12 from the support member 70, as best seen in FIG. 1.The support section 130 defines a central opening 132 that is coaxiallyaligned with the openings 100 and 68 and is adapted to receive andsupport a suitable heavyduty anti-friction bearing assembly, generallydesignated 134. The assembly 134 comprises an inner race 136 that isaxially compressed between a radial shoulder 138 on the shaft 18 and asuitable spacing ring 140 disposed axially inwardly from the pinion gear122, the assembly 134 also comprises an outer race 142 which is adaptedto be retained in place by a suitable annular retaining plate 144fixedly mounted by means of suitable screws, bolts or the like 146circumferentially spaced around the plate 144. Extending interjacent theclamping ring 112 and the anti-friction bearing assembly 134 is anannular shroud or enclosure member 148, one end of which is secured bysuitable screws, bolts, or the like 150 to the bearing assembly 134,while the opposite end thereof terminates adjacent the ring 112 in themanner best illustrated in FIG. 3. The shroud 148 defines a dischargeport 152 which is adapted to cooperate with an axially extending fluidpassage 154 extending coaxially through the interior of the shaft 18 incommunicating lubricating oil to the clutch-brake unit of the presentinvention in a manner later to be described.

Briefly, in operation, the flywheel is adapted to be rotated throughsuitable rotation of a plurality of V- belts (not shown) peripherallyengaged therewith. Rotation of the flywheel 20 is adapted to beselectively transmitted via the clutch-brake unit 10 of the presentinvention to the drive shaft 18 which in turn transmits rotative powerto the pinion gear 122. As will hereinafter be described in detail, theclutch-brake unit 10 normally has the brake elements thereof engaged soas to pre-clude rotation of the drive shaft 18 even though the flywheel20 may be rotating; however, upon actuation of the unit 10, the brakingelements will be released and the clutching elements will be engaged sothat the flywheel 20 will be drivingly connected to the drive shaft 18so that rotational power or torque will be transmitted from the flywheel20 to the pinion gear 122.

Mounted on the drive shaft 18 interiorly of the enclosure member 40 isan annular or ring-shaped hub or support member 156 which defines acentral bore 158 adapted to be contiguously engaged with the peripheryof the adjacent section of the shaft 18. The member 156 is'securedbetween an annular radially outwardly extending shoulder 160 on theshaft 18 and a split retaining ring 162 which is mounted within anannular recess 164 formed around the periphery of the shaft 18. Theouter periphery of the member 156 is formed with the plurality ofradially outwardly extending, circumferentially spaced splinedformations 166 which are adapted to operatively receive and support aplurality of adjacently oriented friction discs, generally designated168. The friction discs 168 are provided with internal openingscomplementary to the formations 166 and adapted for splined engagementtherewith, whereby the discs 168 will be mounted in axially spaced,radially outwardly extending parallel relation, as best seen in FIG. 3.

A series of friction brake plate members, generally designated 170, areeach provided with a plurality of circumferentially spaced, radiallyinwardly extending notches adapted for keyed engagement with a pluralityof longitudinally extending, circumferentially spaced drive lugs 172that are mounted upon a generally conically shaped or tapered lugsupport member 174 disposed coaxially of the shaft 18. The supportmember 174 is formed with an enlarged thickness annular mounting section176 that defines a central opening 177 which is adapted to be secured bymeans of a suitable keyway 178 and annular retaining ring 180 to anaxially extending sleeve-like support section 182 of the support member70. In a preferred construction of the present invention, the supportmember 174 is provided with four circumferentially spaced lugs 172, andthe brake plate members are fonned with a corresponding number ofnotched recesses adapted for engagement with the lugs 172, although itwill be ap' parent that more or less drive lugs 172 may be used whendesired or found necessary. Mounted on the end of the member 156adjacent the support member 174 is an annular, radially extendingabutment ring 184 which defines a radially extending face 186 thatconfronts the friction discs 168 and is fixedly secured to the supportmember 156 by means of a plurality of suitable axially extending screws,bolts or the like 188.

Disposed axially from the member 156 is a second hub or support member190 which is of a generally annular configuration and defines a centralbore 192 which is contiguously engaged with the periphery of the shaft18. The support member 190 is retained upon the shaft 18 by beingaxially positioned between an annular shoulder 194 and the inner race ofthe bearing assembly 102, the support member 190, like the member 156,preferably being keyed or otherwise secured against rotation relative tothe drive shaft 18, as will be apparent. The outer periphery of thesupport member 190 is formed with a plurality of radially outwardlyprojecting, axially extending splined-like formations 196 which aresimilar to the formations 166 and are adapted for splined engagementwith a plurality of axially spaced parallel radially disposed clutchfriction discs 198 which are preferably identical in construction to thediscs 168 and are cooperable with a plurality of axially spaced radiallyextending clutch plate members 200 which are disposed in alternatingrelation with the clutch discs 198. The clutch plate members 200 areexternally notched and are thereby adapted for keyed engagement with aplurality (of preferably four) of axially extending, circumferentiallyspaced drive lugs 202 which are fixedly secured to end wall member 16and project inwardly therefrom, as seen in FIG. 3. Mounted at theaxially outer end of the support member 190 is an annular, radiallyextending abutment ring 204 which may be secured by any suitable meansagainst rotation to the support member 190 and defines a radiallyextending abutment face 206 which is co-operable with the clutchfriction discs 198 in a manner herein-after to be'described.

The support member 190 is formed with a plurality of axially extending,circumferentially spaced bores, generally designated 208, at the axiallyinner end thereof, which bores 208 are adapted to each receive andoperatively support a helical coil spring 210. The springs 210 have theouter ends thereof abutting against end walls 212 defined within thebores 208, while the opposite ends of the springs 210 extend axiallyfrom the adjacent end of the support member 190 are adapted to functionin a manner hereinafter to be described in effecting frictionalengagement between the brake plate members 170, and brake discs 168.

Disposed axially between the plurality of clutch plate members 200 andfriction plate members 170 is an annular piston assembly, generallydesignated 214. The assembly 214 comprises a generally radiallyextending end member 216 which is formed with an axially extendingabutment section 218 that projects toward the friction discs 168 anddefines a radially extending abutment surface 220 engageable with theadjacent of said discs 168. The radially outermost part of the endmember 216 is formed with a reduced thickness flange section 222 whichis secured by a plurality of circumferentially spaced screws, bolts orthe like 224 to an annular, axially extending section 226 of a generallycupped-shaped piston member 228. The member 228 is formed with aradially inwardly extending section 230 that is integrally connected tothe section 226 and is secured by suitable screws, bolts or the like 232to a generally ring-shaped actuating member 234 that extends around theshaft 18 at a position adjacent the clutch friction discs 198. Themember 234 defines a radially extending abutment face 236 that isabuttingly engageable with the adjacent of the friction discs 198 and isthereby cooperable with the face 206 of the abutment ring 204 infrictionally engaging the plate members 200 with the discs 198, as willbe described. A suitable O-ring sealing member or the like 238 isprovided interjacent the axially extending confronting surfaces of themembers 228 and 234, with the member 234 comprising a radially inwardlyextending section 240 disposed in peripheral engagement with the shaft18 and defining a radial face 242 against which the springs 210 abut.

As will later be described in detail, the entire piston assembly 214 isadapted to move axially of the shaft 18 in response to the introductionof pressurized air into the interior thereof. Toward this end, suitableO-ring sealing means 244 is provided around the radially innermostportion of the member 234 which is sealingly engageable with an annularsurface 246 formed around the shaft 18. Similarly, O-ring sealing means248 is provided around the inner periphery of the member 216 and adaptedto sealingly engage an annular surface 250 formed around an annularsupport section 252 of a generally radially disposed partition member260, the section 252 being provided with suitable O-ring sealing means254 adapted to sealingly engage another annular surface 256 defined bythe shaft 18.

The members 216, 228 and 234 define an internal cavity 258, the interiorof which is divided into two axially spaced compartments 262 and 264 bythe partition member 260. The outer periphery of the partition member260 is provided with an O-ring sealing means 266 adapted to sealinglyengage the inner periphery of the axially extending section 226 of themember 228, with a suitable O-ring sealing means 268 being providedinterjacent the radially inner side of the member 260 and an annularrecess 270 formed around the periphery of the shaft 18 interjacent theannular surfaces 246 and 256. It will be seen that the member 260 isfixedly secured relative to the shaft 18 by being axially compressedbetween an annular shoulder 271 formed around the shaft 18 adjacent therecess" 270,

in FIG. 3 against the resistance of the springs 210, until such time asthe face 236 compressingly engages the adjacent of the clutch discs 198and thereby cooperates with the face 206 in frictionally engaging theplurality of clutch plates 200 with the friction discs 198.

In order to admit air into the interior of the compartment 262, theshaft 18 is formed with a central axially extending air passage 272which is communicable through a conventional rotary union 274 located atthe left end of the shaft 18 as viewed in FIG. 3 with a suitable sourceof pressurized air. The opposite (right) end of the passage 272 iscommunicable through a radially outwardly extending passage 276, theradially outermost portion of which is communicable with the interior ofthe compartment 262, as illustrated. The interior of the compartment 264is adapted to be communicable with a suitable air vent through anotheraxially extending air passage 278 which is formed in the drive shaft 18and is communicable through an air passage 280 formed in the member 260and a radially extending passage 282 formed in the shaft 18. The purposeof venting the compartment 264 will be described in connection with theoverall operation of the present invention.

The interior of the cavity 32 is designed to be filled or at leastsubstantially filled with a volume of lubricating oil which functions tominimize the frictional wear between the plates 170, 200 and frictiondiscs 168 and 198, respectively, and to provide a heat transfer functionin maintaining the operating temperature of the unit 10 at a relativelylow level. Toward this end, the unit 10 is provided with an auxillaryoil reservoir 284 provided with a suitable oil pump or the like 286 thatis adapted to function in communicating oil from the reservoir 284through a suitable fluid conduit 288. The conduit 288 is communicablethrough a suitable union 290 with the aforedescribed axially extendingfluid passage 154 formed in the shaft 18, and the passage 154 is in turncommunicable through a radially extending passage 291 with the interioror the bearing assembly 134 and through suitable additionalradiallyextending oil passage means 292 with the interior of the cavity32. Lubricating oil is adapted to be transmitted or communicated out ofthe cavity 32 via suitable internal oil passage 293, one of which isformed in the member and communicable with an oil return conduit 294connected to the reservoir 284. It will be noted that the annularenclosure or shroud member 148 provides a labyrinth sealing arrangement,well known in the art, adjacent the bearing assembly 134, with theannular space provided interjacent the shaft 18 and the shroud 148 beingcommunicable through the discharge port 152 and suitable oil conduitmeans (not shown) with the interior of the reservoir 284 so that anyresidual oil within said annular chamber will be communicated back tothe reservoir.

By way of example, the unit 10 of the present invention is shown in FIG.4 in a typical operational environment, wherein the pinion gear 122 ismeshingly engaged with an associated intermediate gear 296 rotatablymounted on a shaft 298. The shaft 298 is suitably supported within thesupport structure and is provided with drive gears 300 and 302 on theends thereof, which gears 300, 302 are drivingly engageable withassociated gears 304, 306, respectively, mounted on the ends of asuitable crankshaft 308 that is connected to an associated end slidemechanism 310 via conventional connecting rods 312. It will be seen thatthe torque transmitting elements of the clutch are characterized by analternate arrangement of the plurality of clutch plate members 200 andfriction discs 198, with one of the discs 198 being disposed adjacentthe face 206 and another of said discs being disposed adjacent the face236. The torque transmitting portion of the brake is characterized in asimilar manner by an alternate arrangement of the plurality of brakeplate members 170 and friction discs 168, with one of the discs 168being disposed adjacent the face 220 and another thereof being disposedadjacent the face 186.

Assuming the initial condition that lubricating oil is circulating toand from the reservoir 284 via the oil passages 154, 291, 292 and 293,and further assuming that the passages 272 and 276 are communicable witha suitable source of pressurized air, at such time as it is desired toengage the clutch, the aforesaid pressurized air is communicated throughthe passages 272 and 276 into the interior of the compartment 262,thereby forcing the piston assembly 214 toward the right in FIG. 3against the resistance of the plurality of springs 210. Such movement ofthe assembly 214 will effect simultaneous longitudinal movement of thefaces 236 and 220, thereby accomplishing two functions. First of all,the face 236 will cooperate with the face 206 in frictionally engagingthe plurality of discs 198 with the members 200, whereby to drivinglyconnect the flywheel to the drive shaft 18. Secondly and simultaneously,the aforesaid longitudinal movement of the assembly 214 causes the face220 to move longitudinally away from the adjacent disc 168, therebyreleasing the brake in order to permit rotation of the shaft 18.Accordingly, rotation of the flywheel 20, via any suitable V-drive beltsor the like (not shown) will be transmitted through the drive shaft 18to the pinion gear 122, and thereafter through the environmental gearstructure shown in FIG. 4 to operate the end slide mechanism 310 or thelike. At such time as the pressure within the compartment 262 isrelieved, the plurality of springs 210 become operable to longitudinallybias the entire piston assembly 214 toward the left in FIG. 3, with theresult that the face 236 will move away from engagement with theadjacent disc 198 in order to release the clutch, and simultaneously,the face 220 will cooperate with the face 186 in frictionally engagingthe plurality of discs 168 and members 170, thereby engaging the braketo preclude any rotary motion of the flywheel 20 from being transmittedto the drive shaft 18 and hence to the pinion gear 122 mounted thereon.If desired, the vent passages 280, 282 and 278 may be made communicablewith a suitable source of pressurized air which will function, viasuitable air valving, in aiding or supplementing the springs 210 inbiasing the piston assembly 214 toward the position engaging the brakeand releasing the clutch.

It will be noted that the sides of the partition member 260 confrontingthe compartments 262 and 264 are of substantially equal effective areas.With this construction, upon reciprocal movement of the piston assembly214 relative to the partition member 240, a relatively small amount ofair will be displaced through the vent air passages 280, 282 and 278 dueto the balanced conditions of the surface areas on the opposite sides ofthe member 260. Accordingly, the present invention ob viates the needfor any expensive high pressure seals or the like which would benecessary in the case where a large amount of air was expended from theunit 10 during operation thereof.

One particularly important feature of the present invention resides inthe fact that effective cooling or heat dissipation is achieved withoutthe need for any ancillary forced air fans or the like. The reason forthis resides in the fact that during rotation of the flywheel 20, themembers 16, 40 and 14, which constitute the side walls of the cavity 32,are rotating through the ambient air conditions, with the fins or ribs64, 66 creating a substantial amount of air circulation or turbulenceduring rotation thereof. The lubricating oil which is contained withinthe cavity 32 is circulated radially outwardly therewithin under theinfluence of the centrifugal force created upon rotation of the flywheel20, with the result that such oil continuously circulates adjacent theouter wall of the cavity 32 where the heat of the oil is effectivelydissipated. It will be noted that if an auxiliary heat dissipating meansis deemed necessary, the oil reservoir 284 may be provided with anysuitable type of heat exchanger well known in the art, and thatconversely, in the event of relatively small amount of heat dissipationis required, for example, wherein the unit 10 is of a relatively smallsize and capacity, the interior of the cavity 32 may be merely madecommunicable with a suitable reservoir of oil, thereby obviating theneed for oil circulating system as shown herein.

Additional features of the present invention reside in the fact that theentire clutch-brake unit 10 may be preassembled on the drive shaft 18preparatory to the flywheel 20 being operatively positioned and mounted.Thus, the unit 10 may be thoroughly adjusted, tested and generallyplaced in a workable position without the presence of the flywheel 20,thereby considerably facilitating installation of the present invention.It will be also noted that the flywheel 20 may be attached oroperatively connected to the unit 10 in a variety of different ways, aswill be apparent to the skilled artisian, and the present invention isnot intended to be limited to any specific manner in which the flywheelis operatively mounted, other than the flywheel being disposed in heatconducting relation with respect to the interior of the cavity 32 sothat rotation of the flywheel will function in effectively dissipatingthe high temperature conditions attendant within the cavity 32 duringoperation of the unit 10.

The first embodiment of the unit 10 of the present invention will beseen to have a wide variety of different applications, from extrudingdevices, bolt making machines, and virtually all types of flywheel typemetal forming or stamping presses, with the present invention findingparticularly useful application in replacing conventional so-called dryclutch presses heretofore known in the art so that such presses may bereadily converted or up-dated through the installation of theclutch-brake unit 10 of the present invention.

With reference now to FIG. 5 of the drawings, a second embodiment of theclutch-brake unit is indicated generally at 10', being generally similarin design and operation to the unit 10 of the first embodiment, butadapted for applications requiring less torque capacity and particularlyadapted for use with small stamping presses and the like. For purposesof clarity, all component parts of the second embodiment which areeither common, or substantially similar, to the first embodiment aredesignated by like numerals having a prime suffix.

The clutch-brake unit in accordance with the present invention, is showngenerally as comprising a rotatable housing 300 having end walls 302 and304 which are spaced axially or longitudinally along a rotatable driveshaft, generally designated by the numeral 306. The housing 300 forms aninner hub assembly for operatively connecting a driving member, such asa rotatable flywheel, sheave, sprocket, gear, or the like, and generallydesignated 308, to the shaft 306, with the driving member 308 comprisingan outer peripheral portion 310 and an inwardly extending annular flangeportion 312. The flange portion 312 is fixedly connected to an outwardlyextending flange 314 disposed on an outer surface of the housing 300 bymeans of a plurality of circumferentially spaced, axially extendingscrews, bolts, or the like 316.

The housing 300 further includes a central axially extending bore 318spaced radially outwardly from the periphery of the shaft 306 anddefining one marginal wall portion of an internal cavity 320 withinwhich are located the clutch and brake elements of the presentinvention. One axial end of the cavity 320 is closed by an end enclosuremember 322 which is fixedly secured by suitable screws, bolts or thelike 323 to the housing 300, with suitable gasket means, or the like,324 being provided between an annular, radially extending shoulder 326formed on the enclosure member 322 and the axial outer end of thehousing 300.

The member 322 defines a central opening 68' which is arranged coaxiallyof the drive shaft 306 and the periphery of which is spaced radiallyoutwardly from the outer surface thereof. Disposed between the innerperiphery of the opening 68' and the outer periphery of the drive shaft306 is an annular, axially extending portion of a quill member,generally designated by the numeral 342. The inner end of the quillmember extends axially inwardly from the end wall member 322 and definesan annular axially extending shoulder 72 upon which the inner race of ananti-friction bearing assembly 74' is mounted. The outer race of theassembly 74' abuts against an annular shoulder 76 defined around theinner periphery of the enclosure member 322, with the result that themembers 322 and 300, and including the driving member 308, are rotatablysupported relative to the quill member 342, the member 342 havingmounting feet (not shown) which are adapted to be bolted to a suitablesupport attached to the machine frame. The support may be of anysuitable construction which is of a relatively rugged, heavy-duty designas is necessary and conventional in rotatably supporting the unit 10'.Together with supporting the bearing assembly 74', the quill member 342also supports another anti-friction bearing assembly, generallydesignated 82, the inner race of which is engaged with an annularshoulder 84' formed around the adjacent end of the drive shaft 306, andthe outer race of which is received within an annular recess 81 formedaround the inner periphery of the quill member 342. The bearing assembly82, together with suitable fluid sealing means, such as an annular lipseal or the like 86, is positively retained in place in the end of thequill member 342 by means of a suitable snap ring 88' which is removablysecured in a suitable groove 344 in the member 342. The inner race ofthe bearing assembly 82 is also preferably secured upon the inner end ofthe drive shaft 306 by being axially retained between a radiallyoutwardly extending abutment wall 94 defined by the shaft 306 and asuitable snap retaining ring 96' that engages a suitable annular groovedisposed in the shaft 306.

The end of the cavity 320, opposite that which is closed by theenclosure member 322 is adapted to be closed by an inwardlyextendingflange portion 328 of the housing 300, and a radial shoulder330 formed on a clutch spider member 332. The clutch spider member 332is formed with a radially outwardly extending flange section 334, whichsection 334 is fixedly secured by means of a plurality ofcircumferentially spaced, axially extending suitable screws, bolts orthe like, 336, to the radially inwardly projecting flange 328 of thehousing 300, suitable fluid-tight gasket means 338 being providedbetween the confronting sides of the flange 334 and flange portion 328.Additionally, the housing member 300 is preferably provided withcircumferentially spaced, axially extending ribs or fins, generallydesignated 340 for purposes of heat dissipation, as will later bedescribed in detail.

The clutch spider member 332 defines a central opening 100' that iscoaxially aligned with the opening 68' and through which one end of thedrive shaft 306 extends. The shaft 306 is rotatably supported relativeto the opening 100' by means of an anti-friction bearing assembly 102',the inner race of which is seated on an annular shoulder 344 defined onan outer surface of the shaft 306. The outer race of the bearingassembly 102' is adapted to be axially retained between an annularshoulder formed around the periphery of the opening 100' and an annularsnap ring 112 that is secured in a groove 347' defined and suitablyspaced in the opening 100'. Also, suitable lip sealing means or the likeis provided between the inner periphery of the clutch spider member 332and the outer periphery of the shaft 306.

The drive shaft 306 extends axially outwardly from the spider clutch 332and is provided, at thev axially outer end thereof, with a suitablecompanion flange, generally designated 122, which may be secured bymeansof suitable nuts and bolts 345 to a complementing flange 346operatively connected to the equipment or machinery to be driven.

Briefly, in operation, the driving member 308 is adapted to be rotatedby any suitable means complementary therewith. Rotation of the drivingmember 308 is adapted to be selectively transmitted via the clutch-brakeunit 10' of the second embodiment of the present invention, to the driveshaft 306, which in turn transmits rotative power to the equipment ormachinery to be driven. As will hereinafter be described in detail, theclutch-brake unit 10 normally has the brake elements thereof engaged soas to preclude rotation of the drive shaft 306, even though the drivingmember 308 may be rotating; however, upon actuation of the unit 10', thebraking elements will be released and the clutching elements will beengaged so that the driving member 308 will be drivingly connected tothe drive shaft 306 so that rotational power or torque will betransmitted from the driving member 308 to thecomplementing flange 346and drive shaft of the equipment to be driven.

Mounted on the drive shaft 306 interiorly of the enclosure member 322 isan annular or ring-shaped hub or support member 156' which defines acentral bore 158' adapted to be contiguously engaged with the peripheryof the adjacent section of the shaft 306. The member 156' is securedbetween an annular radially outwardly extending shoulder 160' on theshaft 306 and a suitable snap retaining ring 162' which is seated withinan annular groove or recess 164 formed around the outer periphery of theshaft 306. The outer periphery of the member 156 is formed with theplurality of radially outwardly extending, circumferentially spacedsplined formations 166 which are adapted to operatively receive andsupport a plurality of adjacently oriented friction discs, generallydesignated 168'. The friction discs 168 are provided with internalopenings complementary to the formations 166 and adapted for splinedengagement therewith, whereby the discs 168' will be mounted in axiallyspaced, radially outwardly extending parallel relation.

A series of friction brake plate members, generally designated 170', areeach provided with a plurality of circumferentially spaced, radiallyinwardly extending notches adapted for keyed engagement with a pluralityof longitudinally extending, circumferentially spaced drive lugs 172that are mounted upon a generally conically shaped or taperedbrake-spider member 174 disposed coaxially of the shaft 306. Thebrake-spider member 174' is formed with an enlarged annular mountingsection 176' that defines a central opening 177' which is adapted to besecured by means of a suitable keyway 178' and an annular snap ring 180'to an axially extending sleeve-like support section 182 of the quillmember 342. In a preferred construction of the present invention, thebrake-spider member 174 is provided with four circumferentially spacedlugs 172, and the brake plate members 170 are formed with acorresponding number of notched recesses adapted for engagement with thelugs 172, although it will be apparent that more orless drive lugs 172'may be used when desired or found necessary. Mounted on the end of themember 156' adjacent the brake-spider member 174' is an annular,radially extending abutment ring 184', which defines a radiallyextending face 186' that confronts the friction discs 168', and isfixedly secured to the support member 156' by means of a plurality ofsuitable axially extending screws, bolts or the like 188'.

Disposed axially to the right of the member 156, as illustrated in FIG.5, is a disc support portion 190 of the shaft 306 having an outerperiphery formed with a plurality of radially outwardly projecting,axially extending splined-like formations 196', which are similar to theformations 166' of support member 156', and are adapted for splinedengagement with a plurality of axially spaced, parallel, radiallydisposed, clutch friction discs 198'. The discs 198, which arepreferably identical in construction to the discs 168, are cooperablewith a plurality of axially spaced radially extending clutch platemembers 200 which are disposed in alternating relation with the clutchdiscs 198. The clutch plate members 200 are externally notched andadapted for keyed engagement with a plurality (of preferably four) ofaxially extending, circumferentially spaced drive lugs 202' which areintegral to the clutchspider member 332 and project inwardly therefrom.Mounted at the axially outer end of the disc support portion 190' is anannular, radially extending abutment ring 204' which may be secured byany suitable means against rotation to the support portion 190, anddefines a radially extending abutment face 206 which is cooperable withthe clutch friction discs 198' in a manner hereinafter to be described.

Disposed axially between the plurality of clutch plate members 200 andfriction plate members is an annular piston assembly, generallydesignated 214'. The assembly 214' comprises a generally radiallyextending end member 216' which is formed with an axially extendingabutment section 218' that projects toward the friction discs 168' anddefines a radially extending abutment surface 220 engageable with theadjacent of said discs 168. The radially outermost part of the endmember 216' is formed with a reduced thickness flange section 222 whichis secured by a plurality of circumferentially spaced screws, bolts orthe like 224' to an annular, axially extending section 226' of agenerally cup-shaped piston member 228'. The member 228' is formed witha radially extending portion 230 that is integrally connected to thesection 226, and also integrally to a generally ring-shaped actuatingportion 234' that extends around the shaft 306 at a position adjacentthe clutch friction discs 198. The portion 234' defines a radiallyextending abutment face 236' that is abuttingly engageable with theadjacent of the friction discs 198' and is thereby cooperable with theface 206' of the abutment ring 204' in frictionally engaging the platemembers 200' with the discs 198', as will subsequently be described.

As will later be described in detail, the entire piston assembly 214 isadapted to move axially of the shaft 306 in response to the introductionof pressurized air into the interior thereof. Toward this end, asuitable O- ring sealing means 244' is provided around the radiallyinnermost portion of the piston 228' which is sealingly engageable with.an annular surface 246 formed around the shaft 306. Similarly, an O-ringsealing means 248' is'provided around the inner periphery of the member216' and adapted to sealingly engage an annular surface 250' formedaround an annular support section 252 of a generally radially disposedpartition member 260', the section 252' being provided with suitableO-ring sealing means 254' adapted to sealingly engage another annularsurface 256 defined by the shaft 306.

The members 216 and 228' define an internal cavity 258, the interior ofwhich is divided into two axially spaced compartments 262 and 264' bythe partition member 260'. The outer periphery of the partition member260' is provided with an O-ring sealing means 266' adapted to sealinglyengage the inner periphery of the axially extending section 226 of themember 228, with a suitable O-ring sealing means 268' being providedinterjacent the radially inner side of the member 260 and an annularrecess 270' formed around the periphery of the shaft 306. It will beseen that the member 260' is fixedly secured relative to the shaft 306by being axially compressed between an annular shoulder 271' formedaround the shaft 306 adjacent the recess 270, and the axially adjacentend of the support member 156 which is in turn secured in place by thesnap ring 162'.

The end member 216 and the partition member 260 are formed with aplurality of axially aligning, circumferentially spaced blind bores,generally designated 208' and 209' respectively, receiving andoperatively supporting a plurality of helical coil springs 210. Theouter ends of the springs 210' abut against a pair of annular shaped endwalls 212' and 213' as defined by the bores 208 and 209' respectively.The springs 210' and the partition member 260 are adapted to function ina manner hereinafter to be described in effecting frictional engagementbetween the brake plate members 170', and the brake discs 168'. Toprovide an equal surface on both sides of the partition member 260', aradial extending ridge or rim 350 projects outwardly therefrom, on theradial side surface opposite the bore 209 and is adapted to engage acomplementing ringshaped groove 352 disposed in an adjacentcomplementary face of the piston member 228'.

Briefly in operation of the present invention, the plurality of springs210' urge the assembly 214' toward the left, as illustrated in FIG. 5,whereby the face 220' cooperates with the face 186' in compressinglyengaging the friction discs 168' and brake plates 170'. Pressurized airis intended to be admitted into the compartment 262, whereby the entireassembly 214' is biased or urged toward the right against the resistanceof the springs 210', until such time as the face 236' compressinglyengages the adjacent of the clutch discs 198', and thereby cooperateswith the face 206" in frictionally engaging the plurality of clutchplates 200 with the friction discs 198'.

In order to admit air into the interior of the compartment 262', theshaft 306 is formed with a central axially extending air passage 272'which is communicable through a conventional rotary union 274' locatedat the left end of the shaft 306, as viewed in FIG. 5, with a suitablesource of pressurized air. The opposite (right) end of the passage 272'is communicable through a radially outwardly extending passage 276, theradially outermost portion of which is communicable with the interior ofthe compartment 262, as illustrated. The interior of the compartment 264is adapted to be communicable with a suitable air vent through anotheraxially extending air passage 278' which is formed in the drive shaft306 and is communicable through an air passage 280' formed in the member260' and a radially extending passage 282' formed in the shaft 306. Thepurpose of venting the compartment 264' will be described in connectionwith the overall operation of the present invention.

The interior of the cavity 320 is designed to be filled or at leastsubstantially filled with a volume of lubricating oil which functions tominimize the frictional wear between the plates 170', 200 and frictiondiscs 168' and 198', respectively, and to provide a heat transferfunction in maintaining the operating temperature of the unit 10 at arelatively low level. Toward this end, the unit 10' preferably includesa suitable radially extending bore 354 located in the quill member 342,wherein the lubricating oil may be introduced into the cavity 320 of theunit 10'. The lubricating oil system preferably includes an expansiontank (not shown) which includes a breather to keep the internal cavity320 completely filled with oil.

Assuming an initial condition wherein the lubricating oil completelyfills the cavity 320 under the influence of a fluid connection from theexpansion tank, and further assuming that the passages 272' and 276arecommunicable with a suitable source of pressurized air, at such time asit is desired to engage the clutch, the aforesaid pressurized air iscommunicated through the passages 272' and 276 into the interior of thecompartment 262', thereby forcing the piston assembly 214' toward theright as illustrated in FIG. 5, against the resistance of the pluralityof springs 210. Such movement of the assembly 214' will effectsimultaneous longitudinal movement of the faces 236' and 220' wherebythe face 236' will cooperate with the face 206' to frictionally engagethe plurality of discs 198 with the members 200' and drivingly connectthe driving member 308 to the drive shaft 306, and simultaneously theface 220' will move longitudinally away from the adjacent disc 168',thereby releasing the brake in order to permit rotationof the shaft 306.Accordingly, rotation of the driving member 308 via any suitable means(not shown) will be transmitted through the drive shaft 306 to thecomplementing flange 346, and thereafter to the equipment coupledtherewith.

At such time as the pressure within the compartment 262' is relieved,the plurality of springs 210 become operable to longitudinally bias theentire piston assembly 214 toward the left, with the result that theface 236' will move away from engagement with the adjacent disc 198' inorder to release the clutch, and simultaneously, the face 220 willcooperate with the face 186' in frictionally engaging the plurality ofdiscs 168' and members 170', thereby engaging the brake to preclude anyrotary motion of the driving member 308 from being transmitted to thedrive shaft306 and hence to the complementary flange 346 coupledtherewith. If desired, the vent passages 280, 282' and 278 may be madecommunicable with a suitable source of pressurized air which willfunction, via suitable air valving, in aiding or supplementing thesprings 210' in biasing the piston assembly 214 toward the positionengaging the brake and releasing the clutch.

It will be noted that the sides of the partition member 260' confrontingthe compartments 262' and 264' are of substantially equal effectiveareas. With this construction, upon reciprocal movement of the pistonassembly 214, relative to the partition member 260', a relatively smallamount of air will be displaced through the vent air passages 280', 282'and 278' due to the balanced conditions of the surface areas on theopposite sides of the member 260'. Accordingly, the present inventionobviates the need for any expensive high pressure seals or the likewhich would be necessary in the case where a large amount of air wasexpended from the unit 10' during operation thereof.

As previously indicated with reference to the first described embodimentof the present invention, the second embodiment also includes theimportant feature of providing effective cooling or heat dissipationwithout the need for any ancillary forced air fans or the like. Towardthis end, the liousing 300 includes a plurality of ribs 340, andadditionally the end wall 322 is further provided with a plurality ofradial extending fins or ribs 360, both of which are adapted to createasubstantial amount of air circulation or turbulence during rotationthereof. The lubricating oil which is contained with the cavity 320 iscirculated radially outwardly therewithin under the influence of thecentrifugal force created upon rotation of the driving member 308, withthe result that such oil continuously circulates adjacent the outer wallof the cavity 320. The heat of the oil is then effectively dissipated byheat transfer to the housing 300 and to the driving member- 308 which isdrivingly connected therewith.

While it will be apparent that the preferred embodiments illustratedherein are well calculated to fulfill the objects above stated, it willbe appreciated that the present invention is susceptible tomodification, variation and change without departing from the scope ofthe invention.

I claim:

1. A viscous shear clutch brake unit adapted to be mounted in the boreof a flywheel proximate a relatively non-rotatable support structure,the unit comprising: a quill member adapted to be supported by saidsupport structure; a drive shaft having a first end rotatably supportedby said quill member; a first and second series of friction discscarried by said drive shaft; a plurality of brake plates carried by saidquill member and interleaved with one of said series of friction discs;a plurality of clutch plates supported for rotation with said flywheeland interleaved with said other series of friction discs; actuatingmeans for selectively engaging said clutch plates with said other seriesof friction discs while simultaneously releasing said brake plates withsaid one series of friction discs and vice-versa; and a housing assemblyadapted for rotation with said flywheel, and forming a fluid reservoirat least partially surrounding said discs and plates and adapted to beat least partially filled with a cooling liquid media, said assemblyincluding a generally cylindrically shaped housing member having aradially projecting flange section adapted to be connected to the boreof said flywheel in heat transfer relationship therewith, said memberalso including air circulating means located on an outer peripheralsurface thereof for transferring heat away from said unit whereby heatgenerated by engagement of said discs and plates is effectivelydissipated to said flywheel via said housing member and also via saidair circulating means.

2. The clutch brake unit as recited in claim 1 wherein said assemblyalso includes a radially extending end wall rotatably supported by saidquill member and connected to one end of said housing member, said endwall including second air circulating means for dissipating heatgenerated by said unit.

3. The clutch brake unit as recited in claim 1 wherein said aircirculating means includes a plurality of circumferentially spaced finslocated about the outer periphery of said housing member.

4. The clutch brake unit as recited in claim 2 wherein said second aircirculating means includes a plurality of radially extending finslocated on an outer surface of said end wall.

5. A viscous shear clutch brake unit adapted to be mounted in the boreof a flywheel proximate a relatively non-rotatable support structure,the unit comprising: a quill member adapted to be supported bysaidsupport structure; a drive shaft having a first end rotatablysupported by said quill member; a housing assembly defining a fluidreservoir and connected to the bore of the flywheel for rotationtherewith, said reservoir adapted to be at least partially filled with aliquid cooling media; a series of radially extending clutch platesdisposed interiorly of said housing assembly and mounted for rotationtherewith; a series of non-rotatable radially extending brake platesdisposed interiorly of said housing member and supported by said quillmember; a series of friction discs mounted on said drive shaft forrotation therewith and adapted for selective frictional engagement withsaid clutch and brake plates; actuating means including a pistonassembly mounted coaxially of said drive shaft and movable axiallythereof, with movement in one direction serving to simultaneouslyfrictionally engage said clutch plates with certain of said frictiondiscs and to release the remaining friction discs from frictionalengagement with said brake plates, and with movement thereof in anotherdirection serving to simultaneously release said clutch plates fromfrictional engagement with said certain friction discs and tofrictionally engage said remaining friction discs with said brakeplates, said piston assembly including an axially stationary partitionmember carried by said drive shaft, and an axially movable enclosuresurrounding said partition member and defining first and secondcompartments on opposite axial sides thereof, at least one of saidcompartments being selectively pressurizable whereby to cause saidassembly to move axially of said drive shaft to effect respectiveengagement and disengagement of said clutch and brake plates with saidclutch and brake discs; and bias means located in the other of saidcompartments for engaging the brake whereby to provide a failsafe in theabsence of selectively pressing said one compartment.

6. The clutch brake unit as recited in claim 5 wherein one of saidcompartments and said partition member each include a plurality ofcircumferentially spaced bores, and wherein said bias means includes aplurality of spring elements, one element being located in each of saidbores.

7. The clutch brake unit as recited in claim 6 wherein the other of saidcompartments includes passage means for providing a substantially equaland opposed surface area relative to said one compartment, and whereinsaid partition members includes protuberance means at least partiallylocated in said passage means for providing substantially equal surfaceareas on opposite sides of said partition member.

8. The clutch brake unit as recited in claim 5 wherein said enclosureincludes first and second abutment faces for respectively engaging saidclutch and brake plates with said friction discs.

9. A viscous shear clutch brake unit adapted to be mounted in the boreofa flywheel proximate a relatively non-rotatable support structure, theunit comprising: a quill member adapted to be supported by said supportstructure; a drive shaft having a first end rotatably supported by saidquill member; a housing assembly adapted for rotation with saidflywheel, and forming a fluid reservoir at least partially surroundingsaid discs and plates and adapted to be at least partially filled with acooling liquid media, said assembly including a generally cylindricallyshaped housing member having a radially projecting flange sectionadapted to be connected to the bore of said flywheel in heat transferrelationship therewith, said member also including air circulating meanslocated on an outer peripheral surface thereof for transferring heataway from said unit whereby heat generated by engagement of said discsand plates is effectively dissipated to said flywheel via said housingmember and also via said air circulating means; a series of radiallyextending clutch plates disposed interiorly of said housing assembly andmounted for rotation therewith; a series of non-rotatable radiallyextending brake plates disposed interiorly of said housing member andsupported by said quill member; a series of friction discs mounted onsaid drive shaft for rotation therewith and adapted for selectivefrictional engagement with said clutch and brake plates; actuating meansincluding a piston assembly mounted coaxially of said drive shaft andmovable axially thereof, with movement in one direction serving tosimultaneously frictionally engage said clutch plates with certain ofsaid friction discs and to release the remaining friction discs fromfrictional engagement with said brake plates, and with movement thereofin another direction serving to simultaneously release said clutchplates from frictional engagement with said certain' friction discs andto frictionally engage said remaining friction discs with said brakeplates, said piston assembly including an axially stationary partitionmember carried by said drive shaft, and an axially movable enclosuresurrounding said partition member and defining first and secondcompartments on opposite axial sides thereof, at least one of saidcompartments being selectively pressurizable whereby to cause saidassembly to move axially of said drive shaft to effect respectiveengagement and disengagement of said clutch and brake plates with saidclutch and brake discs; and bias means located in the other of saidcompartments for engaging the brake whereby to provide a failsafe in theabsence of selectively pressing said one compartment.

10. The clutch brake unit as recited in Claim 9 wherein one of saidcompartments and said partition member each include a plurality ofcircumferentially spaced bores, and wherein said bias means includes aplurality of spring elements, one element being located in each of saidbores.

1. A viscous shear clutch brake unit adapted to be mounted in the boreof a flywheel proximate a relatively non-rotatable support structure,the unit comprising: a quill member adapted to be supported by saidsupport structure; a drive shaft having a first end rotatably supportedby said quill member; a first and second series of friction discscarried by said drive shaft; a plurality of brake plates carried by saidquill member and interleaved with one of said series of friction discs;a plurality of clutch plates supported for rotation with said flywheeland interleaved with said other series of friction discs; actuatingmeans for selectively engaging said clutch plates with said other seriesof friction discs while simultaneously releasing said brake plates withsaid one series of friction discs and vice-versa; and a housing assemblyadapted for rotation with said flywheel, and forming a fluid reservoirat least partially surrounding said discs and plates and adapted to beat least partially filled with a cooling liquid media, said assemblyincluding a generally cylindrically shaped housing member having aradially projecting flange section adapted to be connected to the boreof said flywheel in heat transfer relationship therewith, said memberalso including air circulating means located on an outer peripheralsurface thereof for transferring heat away from said unit whereby heatgenerated by engagement of said discs and plates is effectivelydissipated to said flywheel via said housing member and also via saidair circulating means.
 1. A viscous shear clutch brake unit adapted tobe mounted in the bore of a flywheel proximate a relativelynon-rotatable support structure, the unit comprising: a quill memberadapted to be supported by said support structure; a drive shaft havinga first end rotatably supported by said quill member; a first and secondseries of friction discs carried by said drive shaft; a plurality ofbrake plates carried by said quill member and interleaved with one ofsaid series of friction discs; a plurality of clutch plates supportedfor rotation with said flywheel and interleaved with said other seriesof friction discs; actuating means for selectively engaging said clutchplates with said other series of friction discs while simultaneouslyreleasing said brake plates with said one series of friction discs andvice-versa; and a housing assembly adapted for rotation with saidflywheel, and forming a fluid reservoir at least partially surroundingsaid discs and plates and adapted to be at least partially filled with acooling liquid media, said assembly including a generally cylindricallyshaped housing member having a radially projecting flange sectionadapted to be connected to the bore of said flywheel in heat transferrelationship therewith, said member also including air circulating meanslocated on an outer peripheral surface thereof for transferring heataway from said unit whereby heat generated by engagement of said discsand plates is effectively dissipated to said flywheel via said housingmember and also via said air circulating means.
 2. The clutch brake unitas recited in claim 1 wherein said assembly also includes a radiallyextending end wall rotatably supported by said quill member andconnected to one end of said housing member, said end wall includingsecond air circulating means for dissipating heat generated by saidunit.
 3. The clutch brake unit as recited in claim 1 wherein said aircirculating means includes a plurality of circumferentially spaced finslocated about the outer periphery of said housing member.
 4. The clutchbrake unit as recited in claim 2 wherein said second air circulatingmeans includes a plurality of radially extending fins located on anouter surface of said end wall.
 5. A viscous shear clutch brake unitadapted to be mounted in the bore of a flywheel proximate a relativelynon-rotatable support structure, the unit comprising: a quill memberadapted to be supported by said support structure; a drive shaft havinga first end rotatAbly supported by said quill member; a housing assemblydefining a fluid reservoir and connected to the bore of the flywheel forrotation therewith, said reservoir adapted to be at least partiallyfilled with a liquid cooling media; a series of radially extendingclutch plates disposed interiorly of said housing assembly and mountedfor rotation therewith; a series of non-rotatable radially extendingbrake plates disposed interiorly of said housing member and supported bysaid quill member; a series of friction discs mounted on said driveshaft for rotation therewith and adapted for selective frictionalengagement with said clutch and brake plates; actuating means includinga piston assembly mounted coaxially of said drive shaft and movableaxially thereof, with movement in one direction serving tosimultaneously frictionally engage said clutch plates with certain ofsaid friction discs and to release the remaining friction discs fromfrictional engagement with said brake plates, and with movement thereofin another direction serving to simultaneously release said clutchplates from frictional engagement with said certain friction discs andto frictionally engage said remaining friction discs with said brakeplates, said piston assembly including an axially stationary partitionmember carried by said drive shaft, and an axially movable enclosuresurrounding said partition member and defining first and secondcompartments on opposite axial sides thereof, at least one of saidcompartments being selectively pressurizable whereby to cause saidassembly to move axially of said drive shaft to effect respectiveengagement and disengagement of said clutch and brake plates with saidclutch and brake discs; and bias means located in the other of saidcompartments for engaging the brake whereby to provide a failsafe in theabsence of selectively pressing said one compartment.
 6. The clutchbrake unit as recited in claim 5 wherein one of said compartments andsaid partition member each include a plurality of circumferentiallyspaced bores, and wherein said bias means includes a plurality of springelements, one element being located in each of said bores.
 7. The clutchbrake unit as recited in claim 6 wherein the other of said compartmentsincludes passage means for providing a substantially equal and opposedsurface area relative to said one compartment, and wherein saidpartition members includes protuberance means at least partially locatedin said passage means for providing substantially equal surface areas onopposite sides of said partition member.
 8. The clutch brake unit asrecited in claim 5 wherein said enclosure includes first and secondabutment faces for respectively engaging said clutch and brake plateswith said friction discs.
 9. A viscous shear clutch brake unit adaptedto be mounted in the bore of a flywheel proximate a relativelynon-rotatable support structure, the unit comprising: a quill memberadapted to be supported by said support structure; a drive shaft havinga first end rotatably supported by said quill member; a housing assemblyadapted for rotation with said flywheel, and forming a fluid reservoirat least partially surrounding said discs and plates and adapted to beat least partially filled with a cooling liquid media, said assemblyincluding a generally cylindrically shaped housing member having aradially projecting flange section adapted to be connected to the boreof said flywheel in heat transfer relationship therewith, said memberalso including air circulating means located on an outer peripheralsurface thereof for transferring heat away from said unit whereby heatgenerated by engagement of said discs and plates is effectivelydissipated to said flywheel via said housing member and also via saidair circulating means; a series of radially extending clutch platesdisposed interiorly of said housing assembly and mounted for rotationtherewith; a series of non-rotatable radially extending brake platesdisposed interiorly of said housing membEr and supported by said quillmember; a series of friction discs mounted on said drive shaft forrotation therewith and adapted for selective frictional engagement withsaid clutch and brake plates; actuating means including a pistonassembly mounted coaxially of said drive shaft and movable axiallythereof, with movement in one direction serving to simultaneouslyfrictionally engage said clutch plates with certain of said frictiondiscs and to release the remaining friction discs from frictionalengagement with said brake plates, and with movement thereof in anotherdirection serving to simultaneously release said clutch plates fromfrictional engagement with said certain friction discs and tofrictionally engage said remaining friction discs with said brakeplates, said piston assembly including an axially stationary partitionmember carried by said drive shaft, and an axially movable enclosuresurrounding said partition member and defining first and secondcompartments on opposite axial sides thereof, at least one of saidcompartments being selectively pressurizable whereby to cause saidassembly to move axially of said drive shaft to effect respectiveengagement and disengagement of said clutch and brake plates with saidclutch and brake discs; and bias means located in the other of saidcompartments for engaging the brake whereby to provide a failsafe in theabsence of selectively pressing said one compartment.